US5002160A - Spot-type disc brake with ventilation channel - Google Patents

Spot-type disc brake with ventilation channel Download PDF

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Publication number
US5002160A
US5002160A US07/025,333 US2533387A US5002160A US 5002160 A US5002160 A US 5002160A US 2533387 A US2533387 A US 2533387A US 5002160 A US5002160 A US 5002160A
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US
United States
Prior art keywords
brake
spot
disc
housing
type disc
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
US07/025,333
Other languages
English (en)
Inventor
Rudolf Weiler
Winfried Gerhardt
Wolfgang Schiel
Ludwig Dreilich
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Continental Teves AG and Co oHG
Original Assignee
Alfred Teves GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Alfred Teves GmbH filed Critical Alfred Teves GmbH
Assigned to ALFRED TEVES GMBH, 7 GUERICKESTRASSE, D-6000 FRANKFURT AM MAIN 90, GERMANY A CORP. OF GERMANY reassignment ALFRED TEVES GMBH, 7 GUERICKESTRASSE, D-6000 FRANKFURT AM MAIN 90, GERMANY A CORP. OF GERMANY ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: DREILICH, LUDWIG, GERHARDT, WINFRIED, SCHIEL, WOLFGANG, WEILER, RUDOLF
Application granted granted Critical
Publication of US5002160A publication Critical patent/US5002160A/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/78—Features relating to cooling
    • F16D65/84—Features relating to cooling for disc brakes
    • F16D65/847—Features relating to cooling for disc brakes with open cooling system, e.g. cooled by air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D55/02—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members
    • F16D55/22—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads
    • F16D55/228—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a separate actuating member for each side
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/02—Braking members; Mounting thereof
    • F16D65/04—Bands, shoes or pads; Pivots or supporting members therefor
    • F16D65/092—Bands, shoes or pads; Pivots or supporting members therefor for axially-engaging brakes, e.g. disc brakes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/02—Braking members; Mounting thereof
    • F16D65/04—Bands, shoes or pads; Pivots or supporting members therefor
    • F16D65/092—Bands, shoes or pads; Pivots or supporting members therefor for axially-engaging brakes, e.g. disc brakes
    • F16D65/095—Pivots or supporting members therefor
    • F16D65/097—Resilient means interposed between pads and supporting members or other brake parts
    • F16D65/0973—Resilient means interposed between pads and supporting members or other brake parts not subjected to brake forces
    • F16D65/0974—Resilient means interposed between pads and supporting members or other brake parts not subjected to brake forces acting on or in the vicinity of the pad rim in a direction substantially transverse to the brake disc axis
    • F16D65/0977—Springs made from sheet metal

Definitions

  • the present invention relates to a spot-type disc brake and in particular a spot type disc brake for motor vehicles.
  • Disc brakes of the type disclosed herein are known from the Brake Handbook of Alfred Teves GmbH, 8th revised edition, published by Bartsch-Verlag, Ottobrunn near Kunststoff. With these known disc brakes, which are designed as fixed-caliper disc brakes, problems may occur when they are used as high-performance brakes because of the heat generated during braking.
  • An object of the present invention is to create a spot-type disc brake in which the disadvantageous effect of the heat generated during braking is greatly reduced.
  • essentially circumferential ventilation channel is provided close to the brake disc and intersecting the brake pad shaft accommodating the brake pads.
  • a preferred embodiment of the invention provides that the brake housing is connected stationarily to a part fixed to the vehicle and on each side of the brake disc and includes at least one piston-cylinder-type actuating device.
  • the solution proposed by the invention has a particularly advantageous effect, since here the pressure medium must be guided over the edge of the disc brake to the piston-cylinder-type actuating device.
  • the piston-cylinder-type actuating device is usually arranged inside the wheel dish and this device along with the brake part accommodating it, heat up due to their largely closed arrangement within the wheel dish. Accordingly, the measures proposed by the present invention are particularly effective.
  • the ventilation channel is designed as an opening formed in the housing. It is conveniently arranged on the exit side relative to the direction of rotation of the brake disc. A particularly expedient solution is thus provided when the opening extends or is open in an axial and/or radial direction.
  • An advantageous embodiment of the invention provides that the brake housing is made in two parts and that each part of the housing forms one portion of the ventilation channel.
  • the brake housing conveniently has the usual U-shape with two radially extending legs connected with each other by a bridge portion. At least one radially extending leg is formed with one axial opening. Viewed in radial direction, the opening is arranged close to the brake pads.
  • the brake housing comprises a recess arranged above the brake disc and this recess is bridged by a member forming a pressure fluid conduit for the piston-cylinder-type actuating device. This arrangement forms a heat shield towards the brake disc because the recess is not open towards the brake disc. However, the pressure medium channel running through the member is separated by two air cushions from the heat-radiating brake disc so that there is very little heat transmission.
  • a further embodiment provides that a channel extends in a circumferential direction close to the brake pads and that this channel is of a width in the axial direction that corresponds to the greatest axial dimension of the brake pads when newly installed.
  • this channel extends in a circumferential direction close to the brake pads and that this channel is of a width in the axial direction that corresponds to the greatest axial dimension of the brake pads when newly installed.
  • air can nevertheless flow through the wide channel and along the rear side of the brake pads.
  • narrow projections are provided which project axially into the channel to support the brake pads. The projections are of very little height, in the order of approximately 1 cm, so that the free cross-section is reduced as little as possible.
  • the pad comprises a rear plate provided in the area of the piston with projections, such as knobs or the like, facing the pistons.
  • the projections are expediently manufactured by stamping through from the side of the friction pads.
  • slip chamfers are provided at the lateral edges of the rear plates.
  • FIG. 1 shows a top view of a spot-type disc brake in accordance with this invention
  • FIG. 2 shows a side view of the spot-type disc brake according to FIG. 1 from inside;
  • FIG. 3 shows a side view of the disc brake according to FIGS. 1 and 2 from outside, with the right half broken away;
  • FIG. 4 shows a longitudinal section through the disc brake illustrated in FIGS. 1 to 3;
  • FIG. 5 shows an enlarged view of a piston and brake pad arrangement used in FIGS. 1-4.
  • the fixed-caliper disc brake 2 illustrated in the drawings has a cross-section which in longitudinal section is U-shaped and forms two radially extending legs 4, 6 which are connected with each other by a bridge portion 8.
  • the inner leg 4, that is the one facing the center of the vehicle when installed, comprises two fastening lugs 10, 12 which are provided with threaded bores 14, 16 in order to fasten the brake to a part fixed to the vehicle, for example the steering knuckle.
  • the inner leg 4 accommodates two actuating devices 18, 20 comprising pistons 26, 28 axially slidingly arranged in cylinder bores 22, 24.
  • the opposite outer leg 6 also contains two actuating devices 30, the second actuating device not being visible, which are designed as pistons 34 slidable in cylinder bores 38.
  • a connection 42 for a conduit for the pressure medium is provided on the inner leg 4.
  • a channel 44 extends at an acute angle relative to the axis of the cylinder bore and leads to the circumferential area of the cylinder bore 24 which it intersects in a small area so that pressure medium can be fed to the cylinder bore.
  • a further channel poriton 46 extends as the straight continuation of the channel portion 44 in the leg 4. In the approximate area where the leg 4 meets the bridge protion 8, the channel portion 46 connects with an axially parallel channel portion 48.
  • the channel portion 48 in turn is connected to a channel portion 50 which extends at an acute angle relative to the axes of the cylinder bores.
  • the channel portion 50 leads to the edge of the cylinder bore 38.
  • the cylinder bores 22, 24 on the one hand and 38, 40 on the other hand are connected via connecting channels, one of which, 52, is shown as connecting the cylinder bores 22 and 24.
  • a similar connecting channel connects the bores 38 and 40.
  • the brake housing 2 is designed in two parts of which the joint face runs parallel to the brake disc plane and is located where the channel portion 48 meets the channel portion 50.
  • the two housing parts are held together by four screws 54, 56, 58, and 60 extending perpendicular to the brake disc plane.
  • Stiffening ribs 62, 64, 66, 68 and/or 70, 72, 74, and 76 are formed on the legs 4, 6 in such a way that the brake housing has a stiff, frame-type structure.
  • the stiffening ribs which extend at a small angle to the tangential direction, in the middle part pass over to that part of the legs 4, 6 accommodating the actuating devices.
  • a brake pad shaft 82 is provided in the bridge portion 8 and is formed as an opening of rectangular cross-section in the bridge portion.
  • the rear plates 84, 86 of the brake pads 78, 80 lie against shaft walls 88, 90 that extend parallel to the brake disc plane.
  • the lateral surfaces of the brake pads 78, 80 are supportable on lateral shaft walls 92, 94 extending parallel to the brake disc axis.
  • the shaft walls 92 and 94 have corresponding supporting surfaces.
  • two pad holding pins 96, 98 are provided which extend with play parallel to the brake disc axis through holes (not shown) in the rear plates 84, 86 and are anchored in the shaft walls 88, 90.
  • a cross spring 100 is provided with one leg resting on the rear plates 84, 86 and the other leg gripping under the pad holding pins 96, 98 in order to provide a springy bracing connection of these two parts.
  • an opening 102 is provided on one side of the brake housing 2 beside the pad shaft.
  • the opening 102 has a substantially rectangular form and is arranged with one of its parts in each of the two housing halves. Only axial webs 104, 106 remain of the housing as a consequence of the opening 102, through which webs the screws 54, 56 extend. Viewed in circumferential direction, the opening is radially drawn down to such an extent that air can flow in the circumferential direction.
  • axial openings 108, 110 arranged approximately opposite each other and of substantially the same shape are provided between the stiffening ribs.
  • Corresponding openings 112 are arranged on the opposite side of the brake pad shaft 82 in the legs. On that side of the pad shaft, a recess 116 extending in the area above the brake disc and in part above the brake pads is provided.
  • the recess 116 in top view has an approximately rectangular form and in cross-section is curved as seen particularly in FIG. 3.
  • a member 120 is arranged which bridges the recess 116 in an axial direction and accommodates a part of the channel portion 48.
  • a double air-insulation space is created between the brake disc and the bottom 118, on the one hand, and the bottom 118 and the member 120, on the other hand, so that the pressure medium channel is very effectively protected against heat in that particularly critical area.
  • the member 120 can be connected with the bottom 118 for reasons of casting practice via a narrow connecting section.
  • an air channel extending in a circumferential direction is formed by the brake housing 2.
  • the inflow area of said channel is formed by the brake housing in the area of the openings 102, 108, and 110.
  • the cross-section of the channel is somewhat larger in axial direction than the greatest axial dimension of the brake pads 78, 80 when completely retracted, as will be seen from FIGS. 1 and 4.
  • air can be supplied through the air channel to the rear side of the brake pads 78, 80.
  • projections or noses 122, 124 facing the brake disc are provided at the legs 4, 6, which projections or noses support the brake pads 78, 80 at the radially inner area, as will be seen from FIGS. 3 and 4.
  • the radial height of the noses is relatively little and ranges approximately from 0.8 to 1.2 cm so that the free passage is hindered as little as possible.
  • the brake pads 78, 80 comprise on their rear plates 84, 86 projections in the form of knobs 126 or the like facing the pistons.
  • Said projections can be arranged, for example, in annular form to correspond to the piston front end and can be manufactured by stamping through.
  • slip chamfers 128, 130 are provided adjacent to the lateral supporting surfaces, as illustrated in FIG. 3.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Braking Arrangements (AREA)
US07/025,333 1986-03-13 1987-03-13 Spot-type disc brake with ventilation channel Expired - Fee Related US5002160A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3608317A DE3608317C2 (de) 1986-03-13 1986-03-13 Teilbelag-Scheibenbremse, insbesondere für Kraftfahrzeuge
DE3608317 1986-03-13

Publications (1)

Publication Number Publication Date
US5002160A true US5002160A (en) 1991-03-26

Family

ID=6296209

Family Applications (1)

Application Number Title Priority Date Filing Date
US07/025,333 Expired - Fee Related US5002160A (en) 1986-03-13 1987-03-13 Spot-type disc brake with ventilation channel

Country Status (5)

Country Link
US (1) US5002160A (de)
JP (1) JPS62220724A (de)
DE (1) DE3608317C2 (de)
FR (1) FR2595778A1 (de)
GB (1) GB2187807B (de)

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5238090A (en) * 1989-10-06 1993-08-24 Rolf Weiler Disc brake housing with continuous outside circumferential edge and cooling ribs
US5558183A (en) * 1993-03-19 1996-09-24 Automotive Products, Plc Disk brake
US6357562B1 (en) * 1999-09-11 2002-03-19 Dr. Ing. H.C.F. Porsche Aktiengesellschaft Aerodynamic wheel-bearing housing
US6446766B1 (en) * 1998-12-31 2002-09-10 Freni Brembo S.P.A. Disk brake for motor vehicles and the like
US20040222050A1 (en) * 2001-12-10 2004-11-11 S.A. Beringer Vehicle braking device
US20050284708A1 (en) * 2002-01-14 2005-12-29 Joachim Christ Cooling arrangement for brake caliper
US20080023276A1 (en) * 2003-12-30 2008-01-31 Michael Schorn Caliper For A Disk-Brake
US20080053759A1 (en) * 2006-09-06 2008-03-06 Jonathan Paul Tait Disc brake caliper and a method of manufacturing a disc brake caliper
US20080067018A1 (en) * 2006-09-19 2008-03-20 Alcon Components Limited Brake disk
US20100101899A1 (en) * 2008-10-29 2010-04-29 Finkel Brian G Brake caliper including heat pipes
US20180328431A1 (en) * 2015-11-02 2018-11-15 Freni Brembo S.P.A. Disc brake calliper body
US10280995B2 (en) * 2017-01-05 2019-05-07 Akebono Brake Industry Co., Ltd Reinforced caliper housing
US11331945B2 (en) * 2018-04-17 2022-05-17 Audi Ag Wheel carrier assembly for a motor vehicle
US11535210B2 (en) * 2020-04-28 2022-12-27 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Wheel carrier assembly for a front axle or rear axle of a motor vehicle

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE8801321U1 (de) * 1988-02-03 1988-08-04 Alfred Teves Gmbh, 6000 Frankfurt Festsattel-Teilbelag-Scheibenbremse mit unsymmetrisch geteiltem Gehäuse
DE3833552A1 (de) * 1988-10-01 1990-04-05 Teves Gmbh Alfred Bremsbelag fuer eine teilbelag-scheibenbremse
DE3906162A1 (de) * 1989-02-28 1990-08-30 Teves Gmbh Alfred Festsattel-scheibenbremse mit asymmetrisch geteiltem bremsgehaeuse
JPH0717861Y2 (ja) * 1989-03-07 1995-04-26 スズキ株式会社 ディスクブレーキのキャリパー
DE3910908C2 (de) * 1989-04-05 1994-01-20 Teves Gmbh Alfred Gußstück für eine Teilbelag-Scheibenbremse
DE4127113A1 (de) * 1991-08-16 1993-02-18 Teves Gmbh Alfred Bremsbacke fuer eine teilbelagscheibenbremse
DE4401843C2 (de) * 1994-01-22 2003-04-30 Continental Teves Ag & Co Ohg Schwimmsattel für Scheibenbremse
JP4342757B2 (ja) * 2001-12-27 2009-10-14 株式会社日立製作所 ディスクブレーキ
DE102007032967B4 (de) * 2007-07-16 2009-07-09 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Belaghaltesystem und Bremsbelag für eine Scheibenbremse
ITTO20120140A1 (it) * 2012-02-16 2013-08-17 Freni Brembo Spa Corpo pinza per freni a disco
US10539199B2 (en) 2017-01-20 2020-01-21 Akebono Brake Industry Co., Ltd Multi-piston caliper

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1351759A (fr) * 1963-03-13 1964-02-07 Girling Ltd Frein à disque du type à compas pour véhicules
US3208559A (en) * 1963-03-13 1965-09-28 Bendix Corp Brake mechanism and means to cool same
DE1213178B (de) * 1963-04-22 1966-03-24 Girling Ltd Hydraulisch betaetigte Teilbelagscheibenbremse
GB1112906A (en) * 1964-08-12 1968-05-08 Bendix Corp Improvements in or relating to disc brakes
GB1216809A (en) * 1968-06-21 1970-12-23 Gen Motors Corp Disc brake caliper bodies
GB1223412A (en) * 1966-12-23 1971-02-24 Autela Components Ltd Formerly Improvements in and relating to disc brake pads
US3637053A (en) * 1970-03-30 1972-01-25 Disco Ind Inc Disc brake apparatus
GB1262263A (en) * 1968-04-05 1972-02-02 Girling Ltd Improvements in or relating to vehicle disc brakes
US3729069A (en) * 1971-06-28 1973-04-24 Bendix Corp Disc brake rotor wiper and noise suppressor
DE2618990A1 (de) * 1975-04-30 1976-11-11 Girling Ltd Bremsbacke fuer eine fahrzeugscheibenbremse
US4031986A (en) * 1974-03-25 1977-06-28 Thompson Tom H Disk brake construction having stamped support
GB2036214A (en) * 1978-11-16 1980-06-25 Tokico Ltd Disc brake
GB2087997A (en) * 1980-11-21 1982-06-03 Toyota Motor Co Ltd Caliper housing in a disc brake
US4440270A (en) * 1981-11-02 1984-04-03 The B. F. Goodrich Company Brake apparatus
DE8236515U1 (de) * 1982-12-27 1984-06-07 Lucas Industries P.L.C., Birmingham, West Midlands Scheibenbremse fuer fahrzeuge
DE3438142A1 (de) * 1984-10-18 1986-04-24 Hermann Dr.-Ing. 3302 Cremlingen Klaue Bremsgehaeuse fuer vollbelagscheibenbremsen, insbesondere fuer kraftfahrzeuge
DE3440324A1 (de) * 1984-11-05 1986-05-15 Klaue, Hermann, Dr.-Ing., 3302 Cremlingen Hydraulische betaetigungsvorrichtung fuer kraftfahrzeug-vollbelagscheibenbremsen
GB2181199A (en) * 1985-10-03 1987-04-15 Teves Gmbh Alfred Brake disc

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GB123412A (en) * 1918-02-26 1919-02-26 John Stopford Harrison Improvements in or relating to Grain Ploughs and the like.
DE1913910U (de) * 1965-01-29 1965-04-15 Clark Maschinenfabrik G M B H Scheibenbremse, insbesondere fuer kraftfahrzeuge.
FR2505280A1 (fr) * 1981-05-08 1982-11-12 Valeo Dispositif de refroidissement pour une roue de vehicule automobile ayant un frein

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US3208559A (en) * 1963-03-13 1965-09-28 Bendix Corp Brake mechanism and means to cool same
DE1213178B (de) * 1963-04-22 1966-03-24 Girling Ltd Hydraulisch betaetigte Teilbelagscheibenbremse
GB1112906A (en) * 1964-08-12 1968-05-08 Bendix Corp Improvements in or relating to disc brakes
GB1223412A (en) * 1966-12-23 1971-02-24 Autela Components Ltd Formerly Improvements in and relating to disc brake pads
GB1262263A (en) * 1968-04-05 1972-02-02 Girling Ltd Improvements in or relating to vehicle disc brakes
GB1216809A (en) * 1968-06-21 1970-12-23 Gen Motors Corp Disc brake caliper bodies
US3637053A (en) * 1970-03-30 1972-01-25 Disco Ind Inc Disc brake apparatus
US3729069A (en) * 1971-06-28 1973-04-24 Bendix Corp Disc brake rotor wiper and noise suppressor
US4031986A (en) * 1974-03-25 1977-06-28 Thompson Tom H Disk brake construction having stamped support
DE2618990A1 (de) * 1975-04-30 1976-11-11 Girling Ltd Bremsbacke fuer eine fahrzeugscheibenbremse
GB2036214A (en) * 1978-11-16 1980-06-25 Tokico Ltd Disc brake
GB2087997A (en) * 1980-11-21 1982-06-03 Toyota Motor Co Ltd Caliper housing in a disc brake
US4440270A (en) * 1981-11-02 1984-04-03 The B. F. Goodrich Company Brake apparatus
DE8236515U1 (de) * 1982-12-27 1984-06-07 Lucas Industries P.L.C., Birmingham, West Midlands Scheibenbremse fuer fahrzeuge
DE3438142A1 (de) * 1984-10-18 1986-04-24 Hermann Dr.-Ing. 3302 Cremlingen Klaue Bremsgehaeuse fuer vollbelagscheibenbremsen, insbesondere fuer kraftfahrzeuge
DE3440324A1 (de) * 1984-11-05 1986-05-15 Klaue, Hermann, Dr.-Ing., 3302 Cremlingen Hydraulische betaetigungsvorrichtung fuer kraftfahrzeug-vollbelagscheibenbremsen
GB2181199A (en) * 1985-10-03 1987-04-15 Teves Gmbh Alfred Brake disc

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Detroit Notebook p. 28, Brake and Front End , 9/1977. *
Detroit Notebook-p. 28, "Brake and Front End", 9/1977.

Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5238090A (en) * 1989-10-06 1993-08-24 Rolf Weiler Disc brake housing with continuous outside circumferential edge and cooling ribs
US5558183A (en) * 1993-03-19 1996-09-24 Automotive Products, Plc Disk brake
US6446766B1 (en) * 1998-12-31 2002-09-10 Freni Brembo S.P.A. Disk brake for motor vehicles and the like
US6357562B1 (en) * 1999-09-11 2002-03-19 Dr. Ing. H.C.F. Porsche Aktiengesellschaft Aerodynamic wheel-bearing housing
US20040222050A1 (en) * 2001-12-10 2004-11-11 S.A. Beringer Vehicle braking device
US7014018B2 (en) * 2001-12-10 2006-03-21 S.A. Beringer Vehicle braking device
US7353919B2 (en) 2002-01-14 2008-04-08 Alcon Components Limited Cooling arrangement for brake caliper
US20050284708A1 (en) * 2002-01-14 2005-12-29 Joachim Christ Cooling arrangement for brake caliper
US8196716B2 (en) * 2003-12-30 2012-06-12 Freni Brembo S.P.A. Caliper for a disk-brake
US20080023276A1 (en) * 2003-12-30 2008-01-31 Michael Schorn Caliper For A Disk-Brake
US20080053759A1 (en) * 2006-09-06 2008-03-06 Jonathan Paul Tait Disc brake caliper and a method of manufacturing a disc brake caliper
US20080067018A1 (en) * 2006-09-19 2008-03-20 Alcon Components Limited Brake disk
US20100101899A1 (en) * 2008-10-29 2010-04-29 Finkel Brian G Brake caliper including heat pipes
US20180328431A1 (en) * 2015-11-02 2018-11-15 Freni Brembo S.P.A. Disc brake calliper body
US10738850B2 (en) * 2015-11-02 2020-08-11 Freni Brembo S.P.A. Disc brake calliper body
US10280995B2 (en) * 2017-01-05 2019-05-07 Akebono Brake Industry Co., Ltd Reinforced caliper housing
US11331945B2 (en) * 2018-04-17 2022-05-17 Audi Ag Wheel carrier assembly for a motor vehicle
US11535210B2 (en) * 2020-04-28 2022-12-27 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Wheel carrier assembly for a front axle or rear axle of a motor vehicle

Also Published As

Publication number Publication date
GB2187807A (en) 1987-09-16
GB2187807B (en) 1990-07-18
JPS62220724A (ja) 1987-09-28
GB8704815D0 (en) 1987-04-08
FR2595778A1 (fr) 1987-09-18
FR2595778B1 (de) 1994-04-22
DE3608317A1 (de) 1987-09-17
DE3608317C2 (de) 1995-03-23

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